Automated lockout system for header

ABSTRACT

Systems and methods for automatically configuring a cutterbar between a flexible configuration and a rigid configuration in response to actuation of a gauge wheel are disclosed. The cutterbar is coupled to the gauge wheel such that extension of the gauge wheel causes the cutterbar to move into the rigid configuration and retraction of the gauge wheel causes the cutterbar to move into the flexible configuration.

FIELD OF THE DISCLOSURE

The present disclosure relates generally to an agricultural header and,particularly, to selectively configuring a cutterbar of an agriculturalheader.

BACKGROUND OF THE DISCLOSURE

Agricultural harvesters use a variety of implements to gather crops. A“draper” or “draper header” is one such type of these implements.Conventional draper headers use conveyors with endless belts to carrycut crop material from leading-edge knives to center regions of theheaders. From there, the cut crop material is conveyed into theharvesters. Once in the harvester, the cut crop material is furtherprocessed by separating grain from unwanted crop material (typicallycalled “material other than grain” or “MOG”).

SUMMARY OF THE DISCLOSURE

A first aspect of the present disclosure is directed to a system forautomatically configuring a cutterbar of an agricultural implement. Thesystem may include a cutterbar, a float arm engaged with the cutterbar,and an actuation system that connects the float arm and the gauge wheel.The float arm may be movable, via the actuation system, in response toone of retraction and extension of the gauge wheel to move the cutterbarbetween a rigid configuration and a flexible configuration. Theactuation system may include a rocker arm that may include a pin andpivotable about a first axis. The rocker arm may be coupled to the floatarm. The actuation system may also include a retainer and a cam coupledto the gauge wheel assembly. The retainer may include a recess thatreleasably receives the pin to selectively lock the pin into the recessand a protrusion. The cam may be moveable with the gauge wheel assemblyto selectively engage the protrusion of the retainer to move theretainer between a locked configuration and an unlocked configuration.

A second aspect of the present disclosure is directed to a method formoving a cutterbar of an agricultural implement between a rigidconfiguration and a flexible configuration in response to articulationof a gauge wheel of the agricultural implement between a retractedconfiguration and an extended configuration. The method may include oneof extending and retracting a gauge wheel of an agricultural implementand simultaneously one of moving the cutterbar into a flexibleconfiguration in response to retraction of the gauge wheel and movingthe cutterbar into a rigid configuration by an actuation system that isoperated in response to retraction of the gauge wheel.

A third aspect of the present disclosure is directed to an agriculturalimplement that automatically configures a cutterbar between a rigidconfiguration and a flexible configuration. The agricultural implementmay include a frame; a gauge wheel assembly coupled to the frame andmoveable between an extended position and a retracted position; a floatarm pivotably coupled to the frame; a cutterbar engaged with the floatarm, the cutterbar moveable between a rigid configuration and a flexibleconfiguration in response to rotation of the float arm; and an actuationsystem that connects the float arm and the gauge wheel assembly. Thefloat arm may be movable, via the actuation system, in response to oneof retraction and extension of the gauge wheel to move the cutterbarbetween the rigid configuration and the flexible configuration. Theactuation system may include a rocker arm comprising a pin and pivotableabout a first axis, a retainer, and a cam coupled to the gauge wheelassembly. The rocker arm may be coupled to the float arm. The retainermay include a recess that releasably receives the pin to selectivelylock the pin into the recess and a protrusion.

The various aspects may include one or more of the following features.When the gauge wheel assembly is in the retracted position, the cam mayengage the protrusion of the retainer to release the pin from therecess, placing the retainer in the unlocked configuration and thecutterbar in the flexible configuration. Extension of the gauge wheelassembly from the retracted position to the extended position may rotatethe cam to release the retainer to cause the retainer to pivot andcapture the pin into the recess, placing the retainer into the lockedconfiguration and the cutterbar in the rigid configuration. A biasingforce may pivot the retainer in response to release by the cam. Thebiasing force may be generated by a compressed spring. Retraction of thegauge wheel assembly from the extended position to the retractedposition may rotate the cam to engage the protrusion of the retainer,causing the retainer to release the pin from the recess, placing theretainer in an unlocked configuration and the cutterbar in the flexibleconfiguration. The actuation system may also include a spring coupled tothe rocker arm. The spring may apply a moment to the rocker arm to pivotthe rocker arm in a direction that moves the pin towards the recess ofthe retainer. The moment applied to the rocker arm by the spring maypivot the rocker arm towards the retainer when weight of the float armis removed from the rocker arm. A retainer assembly may be included. Theretainer assembly may include the retainer, a shaft pivotably coupled tothe retainer, and a spring disposed on the shaft and configured to applya moment to the retainer. The spring may compress in response toengagement of the protrusion of the retainer by the cam, and thecompressed spring may pivot the retainer about a second axis when thecam disengages the protrusion of the retainer.

Additionally, the various aspects may include one or more of thefollowing features. The actuation system may include a rocker arm thatincludes a pin and pivotable about the first axis, a retainer, and a camcoupled to the gauge wheel. The rocker arm may be coupled to the floatarm. The retainer may include a recess that releasably receives the pinto selectively lock the pin into the recess and a protrusion. The cammay be moveable with the gauge wheel assembly to selectively engage theprotrusion of the retainer to move the retainer between a lockedconfiguration and an unlocked configuration. Simultaneously one ofmoving the cutterbar into a flexible configuration in response toretraction of the gauge wheel and moving the cutterbar into a rigidconfiguration by an actuation system that is operated in response toretraction of the gauge wheel may include extending the gauge wheel fromthe retracted position to the extended position; pivoting the cam inresponse to extension of the gauge wheel to disengage the cam from theprotrusion of the retainer; and receiving the pin into the recess inresponse to disengagement of the cam from the protrusion of theretainer, thereby locking the cutterbar into the rigid configuration.The rocker arm may be pivoted in a direction that moves the pin towardsthe recess of the retainer. Pivoting the rocker arm may include applyinga moment to the rocker arm with a spring. Pivoting the rocker arm in adirection that moves the pin towards the recess of the retainer mayinclude removing weight of the float arm from the rocker arm so that amoment applied to the rocker arm is great enough to pivot the rocker armin the direction that moves the pin towards the recess of the retainer.Simultaneously one of moving the cutterbar into a flexible configurationin response to retraction of the gauge wheel and moving the cutterbarinto a rigid configuration by an actuation system that is operated inresponse to retraction of the gauge wheel may include retracting thegauge wheel from the extended position to the retracted position;pivoting the cam in response to retraction of the gauge wheel to engagethe cam with the protrusion of the retainer; and releasing the pin fromthe recess in response to engagement of the cam with the protrusion ofthe retainer, thereby unlocking the cutterbar and placing the cutterbarinto the flexible configuration.

Also, the various aspects may include one or more of the followingfeatures. Extension of the gauge wheel assembly from the retractedposition to the extended position may rotate the cam to release theretainer to cause the retainer to pivot and capture the pin into therecess, placing the retainer into the locked configuration and thecutterbar in the rigid configuration. Retraction of the gauge wheelassembly from the extended position to the retracted position may rotatethe cam to engage the protrusion of the retainer, causing the retainerto release the pin from the recess, placing the retainer in an unlockedconfiguration and the cutterbar in the flexible configuration.

Other features and aspects will become apparent by consideration of thedetailed description and accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

The detailed description of the drawings refers to the accompanyingfigures in which:

FIG. 1 is an oblique view of an example draper header, according to someimplementations of the present disclosure.

FIG. 2 is oblique view of a portion of a frame of an example header,according to some implementations of the present disclosure.

FIG. 3 a detail view of a portion of a frame of an example header,according to some implementations of the present disclosure.

FIG. 4 is cross-sectional view of portions of an example lockout system,according to some implementation of the present disclosure.

FIG. 5 is an oblique view of the lockout system of FIG. 4 .

FIG. 6 is a detailed, cross-sectional view of a portion of the lockoutsystem of FIG. 4 .

FIG. 7 is another detailed, cross-sectional view of a portion of thelockout system of FIG. 4 .

FIG. 8 is a side view of a portion of an example header with anassociated gauge wheel in a retracted position, according to someimplementations of the present disclosure.

FIG. 9 is a side view of the portion of the example header of FIG. 8with the associated gauge wheel in an extended position.

FIG. 10 is a detailed view of an example retainer assembly, according tosome implementations of the present disclosure.

FIG. 11 is a detailed view of another example actuation system,according to some implementation of the present disclosure.

FIG. 12 is another detailed view of the actuation system of FIG. 11 .

FIG. 13 is a detailed cross-sectional side view of the example actuationsystem of FIG. 11 in which the actuation system is in a firstconfiguration.

FIG. 14 is a detailed cross-sectional view of the example actuationsystem of FIG. 11 in which the actuation system is in a secondconfiguration.

FIG. 15 is a detailed cross-sectional view of a portion of an exampleagricultural implement, according to some implementations of the presentdisclosure.

FIG. 16 is another detailed cross-sectional view of the portion of theagricultural implement of FIG. 15 .

DETAILED DESCRIPTION

For the purposes of promoting an understanding of the principles of thepresent disclosure, reference will now be made to the implementationsillustrated in the drawings, and specific language will be used todescribe the same. It will nevertheless be understood that no limitationof the scope of the disclosure is intended. Any alterations and furthermodifications to the described devices, systems, or methods and anyfurther application of the principles of the present disclosure arefully contemplated as would normally occur to one skilled in the art towhich the disclosure relates. In particular, it is fully contemplatedthat the features, components, and/or steps described with respect toone implementation may be combined with the features, components, and/orsteps described with respect to other implementations of the presentdisclosure.

The present disclosure is directed to agricultural implements and,particularly, to draper headers that include automated lockout systemsthat are movable between a flexible configuration and a rigidconfiguration. Although various examples are provided in the context ofdraper headers, the scope of the present disclosure is applicable toother types of agricultural implements. In some implementations, thelockout systems are actuated in response to deployment of gauge wheelsof the header. In the flexible configuration, float arms of the headerare freely pivotable about respective axes, and, in the rigidconfiguration, the float arms are retracted into contact with a portionof the header, thereby providing a cutterbar attached to the float armsin a rigid configuration. Extension of the gauge wheels causes floatarms and cutterbar to move into the rigid configuration. Retraction ofthe gauge wheels causes the float arms and cutterbar to move into theflexible configuration. In some instances, the lockout systems providefor abutting contact between the float arms and another portion of theframe without any adjustment provided either during manufacturing or inthe field, thereby reducing manufacturing and maintenance time andcomplexity. Further, in some implementations, in the rigidconfiguration, torque applied to a lockout tube is reduced to zero orapproximately zero, thereby reducing size, weight, and cost of theheader. Additionally, lockout systems described herein are actuatablefrom a cab of a vehicle. Consequently, an operator avoids having to exitthe cab of a vehicle in order to actuate a lockout system within thescope of the present disclosure.

Words of orientation, such as “up,” “down,” “top,” “bottom,” “above,”“below,” “leading,” “trailing,” “front,” “back,” “forward,” and“rearward” are used in the context of the illustrated examples as wouldbe understood by one skilled in the art and are not intended to belimiting to the disclosure. For example, for a particular type ofvehicle in a conventional configuration and orientation, one skilled inthe art would understand these terms as the terms apply to theparticular vehicle.

For example, as used herein, with respect to an endless belt, unlessotherwise defined or limited, the term “forward” (and the like)corresponds to a forward direction of travel of the belt, with respectto a supporting frame (e.g., a frame of a draper header), during normaloperation of the belt. Likewise, the term “rearward” (and the like)corresponds to a direction opposite the forward direction of travel ofthe belt. In this regard, for example, a “forward facing” feature on anendless belt may generally face in the direction that the belt travelsduring normal operation, while a “rearward facing” feature may generallyface opposite that direction.

Also as used herein, with respect to a header (or components thereof),unless otherwise defined or limited, the term “leading” (and the like)indicates a direction of travel of the header during normal operation(e.g., the forward direction of travel of a harvester vehicle carrying aheader). Similarly, the term “trailing” (and the like) indicates adirection that is opposite the leading direction. In this regard, forexample, a “leading” edge of a cutterbar of a draper header may begenerally disposed at the front of the cutterbar, with respect to thedirection travel of the draper header during normal operation (e.g., ascarried by a harvester vehicle). Likewise, a “trailing” edge of thecutterbar may be generally disposed at the back or a side of thecutterbar opposite the leading edge, with respect to the direction oftravel of the draper header during normal operation.

FIG. 1 shows an example draper header 100 that includes a frame 102 thatsupports a first side conveyor 104, a second side conveyor and 106, anda center conveyor 108. Each of the conveyors 104, 106, and 108 isconfigured as a belt-type conveyor extending over a respectivecircumferential length. The conveyors 104, 106, and 108 include endlessbelts 110, 112, and 114 that are moved in respective loops along theheader 100 by motive devices, such as motors, gears, or internal belts.The conveyors 104 and 106 are disposed on opposing wings 116 and 118,respectively, of the header 100. In the illustrated example, theconveyor 104 includes two endless belts 110, and the conveyor 106 andtwo endless belts 112. In other implementations, the conveyors 104 and106 may include additional or fewer endless belts. Further, although theconveyor 108 is shown as including a single endless belt 114, in otherimplementations, the conveyor 108 may include additional endless belts.The endless belts 110, 112, and 114 are supported on two or more rollersof the respective conveyors 104, 106, and 108. Although the draperheader 100 is illustrated as a rigid or non-folding draper header, thescope of the present disclosure encompasses folding draper headers.

In some implementations the endless belts 110, 112, and 114 may beformed from elastomer-impregnated fabric belts. Generally, the endlessbelts 110 and 112 may be rotated such that upper surfaces of the endlessbelts 110 and 112 move inward along the header 100 in respectivedirections 120 and 122. In this way, material, such as severed cropmaterial, is moved by the endless belts 110 and 112 to the centerconveyor 108, which, in turn, uses the endless belt 114 to move thematerial off of the header 100. For example, the header 100 may offloadthe material onto a harvester vehicle to which the header 100 isattached. The header 100 also includes a cylindrical conveyor 124. Thecylindrical conveyor 124 receives severed crop material from the centerconveyor 108 and carries the crop material rearward (i.e., in adirection 126) through an aperture in the frame 102 located between thecylindrical conveyor 124 and the center conveyor 108 and, ultimately,into the harvester vehicle.

In the illustrated example, various cleats 130 are fixed to the surfaceof each of the endless belts 110, 112, and 114, with the cleats 130generally extending in a direction transverse to the direction of travelof the respective endless belt 110, 112, or 114, e.g., directions 120,122, and 126. In some implementations, the cleat 130 may extend lessthan an entire width of the endless belts 110, 112, and 114. Forexample, one or more of the cleats 130 may extend only partially acrossthe respective width of the endless belts 110, 112, and 114, and,accordingly, may not extend to a leading edge or a trailing edge of thebelts 110, 112, and 114.

The header 100 also includes a cutterbar 132 at a leading edge 133 ofthe header 100. The cutterbar 132 cuts crop material, such as to severcrop material from a field. The cutterbar 132 extends laterally alongthe header 100. In some implementations, the header 100 may also includea leading cover arranged between the cutterbar 132 and the endless belts110, 112, and 114, with the leading cover extending at least partly overa leading edge of at least the belts 110 and 112. As shown in FIG. 1 ,for example, the header 100 includes an elongated row of interlockingcrop ramp segments 134 that extend along the header 100.

As depicted, the header 100 also includes a trailing cover 136, whichmay be in the form of a back sheet deflector or rear frame cover,separated from the crop ramp segments 134 by a width 138. The trailingcover 136 serves to cover and protect various internal components of theheader 100 and also generally defines a trailing end of a crop-carryingregion of the header 100. In some implementations, the cleats 130 extendover the entire width 138. In other implementations, the cleats 130extend over a portion of the width 138.

During a harvesting operation, a harvester vehicle carries the header100 through an agricultural field in a nominal forward direction 140. Asthe header 100 is moved across the field, the cutterbar 132 operates tosever the crops at a location adjacent to the ground. The severed cropmaterial generally falls in a trailing direction (i.e., generallyopposite the direction 140), onto one or more of the three conveyors104, 106, and 108. The conveyor 104 on the wing 118 carries the cropmaterial in the direction 120, using the endless belts 110, toward thecenter of the header 100. The conveyor 106 carries the severed cropmaterial in the direction 122, using the endless belts 112, toward thecenter conveyor 108, and the center conveyor 108 carries the severedcrop material in the direction 126 towards and underneath thecylindrical conveyor 124. The severed crop material from the cylindricalconveyor 124 is transported in the direction 126 through the aperture inthe frame 102 of the header 100 and into the agricultural harvester.

In the illustrated example, the conveyor 104 and the conveyor 106 aresimilarly configured, although the conveyors 104 and 106 carry cropmaterial in opposite directions 120 and 122, respectively. In otherimplementations, the conveyors 104 and 106 can be configureddifferently. Generally, however, the description herein of the conveyor104 is applicable to the conveyor 106, as well as other conveyors ofother implementations.

FIG. 2 is a view of a portion of a frame 200 of a header 202, which maybe similar to the header 100. The portion of the frame 200 illustratedcorresponds to a portion of a wing 204 of the header 202. The wing 204may be similar to wing 118 of the header 100. The frame 200 includes abeam 206 extending laterally along the frame 200. A back section 208 iscoupled to the beam 206 and extends therefrom. The back section 208 alsoextends laterally along the frame 200. An outboard side section 207connects to the beam 206 and the back section 208 and defines a lateralend of the frame 200. A plurality of mounting brackets 210 are alsocoupled to the beam 206. With the header 202 conventionally oriented,the brackets 210 general extend in a direction corresponding to aforward direction. The frame 200 also includes a laterally extendingcross tube 212 that connects to each of the mounting brackets 210. Insome implementations, the cross tube 212 may have a square, rectangular,or circular cross-sectional shape and may define a central passage.However, the cross tube 212 may have other cross-sectional shapes. Floatarms 214 are pivotably coupled to the mounting brackets 210, and acutterbar 216 is coupled to distal ends 218 of each of the float arms214. Similar to the cutterbar 132, the cutterbar 216 is a reciprocatingcutterbar.

In some implementations, the mounting brackets 210 and correspondingfloat arms 214 are laterally separated from adjacent mounting brackets210 and corresponding float arms 214 by approximately 2.5 feet (ft) (0.8meters (m)). In other implementations, the lateral separation 215 may begreater than or less than 2.5 ft (0.8 m). In still otherimplementations, the lateral separation 215 may vary. Thus, in someimplementations, the lateral separation 215 between some adjacentmounting brackets 210 and corresponding float arms 214 may be uniformwhile the lateral separation between other adjacent mounting brackets210 and corresponding float arms 214 may be non-uniform.

With the header 202 in an unsecured or flexible configuration, each ofthe float arms 214 are able to pivot independently of the other floatarms 214. As a result, when the float arms 214 are in contact with theground and propelled over the ground, such as during a harvestingoperation, each of the float arms 214 is able to follow a topography orcontour of the ground. In response to the float arms 214 conformingmovement to the contour of the ground, the cutterbar 216 flexes to alsoconform to the contour of the ground. As a result, a portion of the cropextending from the ground and remaining in a field may be generallyconsistent, e.g., a height by which the crop remaining in field extendsfrom the ground is generally uniform.

In a rigid configuration in which the float arms 214 are held in anabutting relationship against a portion of the frame 200, such as thecross tube 212, the float arms 214 are prevented from following acontour of the ground, and the cutterbar 216 is maintained in agenerally straight and rigid configuration, e.g., the cutterbar 216maintains a generally straight, unbent shape.

The header 202 also includes a lockout system 220 that is operable tomove the float arms 214 and the cutterbar 216 between the flexibleconfiguration and the rigid configuration. In some implementations, theheader 202 includes a lockout system 220 for each wing 204. The separatelockout systems 220 are operable to move the float arms 214 andassociated portion of the cutterbar 216 of one wing between the rigidconfiguration and the flexible configuration independently of the floatarms 214 and associated portion of the cutterbar 216 of the other wing.Thus, in some implementations, the header 202 may include two lockoutsystems 220. In other implementations, the header may include a singlelockout system 220 for all of the wings of the header 202. In stillother implementations, the header 200 may include more than two lockoutsystems.

The lockout system 220 includes a rotatable component, which, in theexample of FIG. 2 , is a lockout tube 222. In some implementations, thelockout tube 222 is in the form of a shaft. The lockout tube 222 extendslaterally along the header 202 through apertures 224 formed in each ofthe mounting brackets 210. The lockout tube 222 is rotatable relative tothe mounting brackets 210 about a centerline 226.

The header also includes gauge wheels 228, as shown in FIG. 3 . In someimplementations, the header 200 includes two gauge wheels 228distributed laterally along each wing of the header 200. In otherimplementations, the header 200 includes fewer or additional gaugewheels 228. FIG. 3 illustrates a single gauge wheel 228, although, asexplained earlier, the scope of the disclosure is not so limited.

A gauge wheel assembly 229 includes the gauge wheels 228 and an arm 230to which the gauge wheels are rotatably coupled. The arms 230 arepivotably coupled to a mounting bracket 210. The gauge wheels assemblies229 are movable between a retracted position and an extended position.An actuation system 231 couples the gauge wheel assembly 229, via arm230, to the lockout tube 222 such that extension or retraction of thegauge wheel, such as by rotation of the arm 230 about axis 234, causesrotation of the lockout tube 222 about the centerline 226. The axis 234extends through a pivot where the arm 230 is coupled to the mountingbracket 210. In the illustrated example, the actuation system 231 is alinkage (shown in more detail in FIG. 4 ) that extends between andcouples the lockout tube 222 and the arm 230.

FIG. 3 is a detail view of a portion of a frame 300 of an example header302 within the scope of the present disclosure. The frame 300 may besimilar to the frame 200. The frame 300 includes a laterally-extendingbeam 304, similar to beam 206, and a mounting bracket 306, similar tomounting bracket 210. A float arm 308 is pivotably mounted to themounting bracket 306. A gauge wheel 310 is coupled to the frame 300. Thegauge wheel 310 is rotatably coupled to an arm 312, and the arm 312 ispivotably mounted to the mounting bracket 306. A lockout tube 314,similar to lockout tube 222, extends laterally though apertures 316formed in the mounting bracket 306. The lockout tube 314 is rotatableabout a centerline 318, similar to centerline 226, that extendslongitudinally along the lockout tube 314. The lockout tube 314 isrotatably coupled to the arm 312 via a linkage 320. In the illustratedexample, the linkage includes three links. However, in otherimplementations, the linkage 320 may include additional or fewer links.The linkage 320 includes a first link 322 fixedly attached to the arm312, a second link 324 pivotably coupled to the first link 322, and athird link 325 fixedly attached to the lockout tube 314 and pivotablycoupled to the second link 324.

The header 302 also includes a lockout system 326 that functions to movethe float arms 308 and associated portions of a cutterbar provided atthe distal ends of the float arms 308 of the header 302 between aflexible configuration and a rigid configuration. The lockout tube 314is connected to the lockout system 326 such that rotation of the lockouttube 314 in a first direction causes the lockout system 326 to lockinglyposition the float arms 308 into the rigid configuration. Conversely,rotation of the lockout tube 314 in a second direction, opposite thefirst direction, causes the lockout system 326 to move the float arms308 from the rigid configuration into the flexible configuration.

Although some implementations include a lockout system, such as lockoutsystem 326 described in more detail below, in other implementations, alockout system may be omitted. Thus, in some implementations, thelockout 314 is coupled directly or indirectly to the float arms 308without the use of a lockout system.

FIG. 4 is a cross-sectional view of additional portions of the lockoutsystem 326. The lockout system 326 also includes a tensioner 400 and alinkage 402 coupled to the lockout tube 314. The tensioner 400 includesa bracket 404, a shaft 406 extending through an aperture 408 in a side410 of the bracket 404, and a biasing component 412 captured on theshaft 406 between the side 410 of the bracket 404 and a flange 414secured to the shaft 406. In some implementations, the flange 414 may besecured to the shaft between a shoulder 416 and a nut 418 threadablyreceived onto the shaft 406. In other implementations, the flange 414may be secured to the shaft 406 in other ways, such as by welding, apress fit, or by being integrally formed onto the shaft 406.

In some implementations, the biasing component 412 is a spring, such asa coil spring. In some implementations, the biasing component 412 is aplurality of biasing components. For example, in some implementations,the biasing component 412 is a plurality of Bellville washers 413stacked along a length of the shaft 406, as shown in FIG. 4 . In someimplementations, the Bellville washers are arranged in pairs, such thata base of each Bellville washer in a pair abuts each other. Pairs of theBellville washers may be arranged adjacent to each other along a lengthof the shaft 406, as shown, for example, in FIGS. 4, 6, and 7 . In someimplementations, 32 Bellville washers may be used. However, additionalor fewer Bellville washers may be used, and the number of Bellvillewashers may vary depending upon, for example, sizes and masses of thedifferent components of a header.

In still other implementations, the biasing component 412 may be orinclude a coil spring. For example, in some instances, the biasingcomponent 412 may include a plurality of coils springs. One or more ofthe coils springs may be received onto the shaft 406. In still otherimplementations, the biasing component 412 may be another type ofspring.

The tensioner 400 is pivotably coupled to the float arm 308 by a pin 420coupled to the float arm 308. In the illustrated example, the pin 420extends through apertures 422 formed in a clevis 424 that is attached tothe float arm 308. The shaft 406 extends through a bore 425 formedthrough the pin 420. A flange 426 captures the shaft 406 onto the pin420. In some implementations, the flange 426 may be a washer secured tothe shaft 406 between a shoulder 428 and a nut 430 threadably receivedonto a threaded portion 432 of the shaft 406. In other implementations,the flange 426 may be secured to the shaft 406 in other ways, such as apress fit or welding, or the flange 426 may be integrally formed on theshaft 406. The shaft 406 also includes an enlarged portion 434 thatabuts against the side 410 of the bracket 404. Engagement between theside 410 and the enlarged portion 434 allows the biasing component 412to be preloaded between the side 410 and the flange 414. In someimplementations, the biasing component 412 may not be preloaded.

The preload applied to the biasing component 412 may be selected toensure a force applied to the float arms 308 of a lockout system 326 bythe biasing component 412 lifts the float arms 308 into abutting contactbetween all of the float arms 308 and a portion of the frame 300, suchas a cross tube similar to cross tube 212 shown in FIG. 2 . Thus, thepreload ensures that a force ultimately provided by the biasingcomponent 412 as the lockout system 326 is moved into the rigidconfiguration fully actuates all of the float arms 308 notwithstandingany variations in the header 302, such as manufacturing variations thatmay otherwise prevent all of the float arms 308 from being in abuttingcontact with the cross tube when the lockout system 326 is in the rigidconfiguration. As a result, lockout systems of the present disclosureare operable to ensure full retraction of all of the float arms of aheader when placed in the rigid configuration without adjustment duringmanufacturing or sometime later in the field, such as by a user ortechnician. Thus, the lockout systems and associated headers of thepresent disclosure reduce maintenance thereto, improves performance ofoperation of the headers, increases productivity of the headers, andreduces costs of operation of the headers.

The linkage 402 includes a first link 436 coupled to the lockout tube314 and a second link 438 pivotably coupled to the first link 436 andthe bracket 404. In the illustrated example, the first link 436 isattached to the lockout tube 314 with a fastener 439, such as a bolt.However, in other implementations, the first link 436 may be attached tothe lockout tube 314 in other ways, such as by welding, interferencefit, an adhesive, or by being integrally formed on the lockout tube 314.Also, in the illustrated example, a nut 441 is used to secure thefastener 439 and the first link 436 to the lockout tube 314.

Referring to FIGS. 4 and 5 , the bracket 404 has a general U-shape, andthe second link 438 includes a first side 440 and a second side 442.Free ends 444 of the bracket 404 are sandwiched between the first andsecond sides 440 and 442 at a first end 445 of the second link 438. Atab 446 formed on the first link 436 is disposed between the first andsecond sides 440 and 442 of the second link 438 at a second end 452 ofthe second link 438. A pin 448 extends through the first and secondsides 440 and 442 at the second end 452 of the second link 438 and thetab 446 of the first link 436 to pivotably couple the first link 436 andthe second link 438. A pin 450 extends between the free ends 444 of thebracket 404 and the first and second sides 440 and 442 at the first end445 of the second link 438 to pivotably couple the second link 438 andthe bracket 404. In some implementations, the pins 448 and 450 may be arod or a fastener, such as a bolt. However, the pins 448 and 450 mayhave other forms to enable the first link 436 to pivot relative to thesecond link 438 and the bracket 404 to pivot relative to the second link438. The float arm 308 is pivotable about a pin 451 that pivotablycouples the float arm 308 to the mounting bracket 306. The pin 451 maybe, for example, a fastener (e.g., a bolt), a shaft, or other componentoperable to permit pivoting movement of the float arm 308 relative tothe mounting bracket 306. FIG. 5 also shows an impact absorber component460 that is attached to the frame 300 of the header 302, such as thecross tube, and contacts a float arm 308 when retracted into the rigidconfiguration. The impact absorber component 460 may be attached to thecross tube with fasteners 462, which may be, for example, bolts, pins,or rivets

As shown in FIGS. 4 through 7 , the second link 438 has an arcuate shapethat provides a relief or recess 437 that receives the lockout tube 314.The recess 437 formed by the arcuate shape receives the lockout tube314, allowing the centerline 318 of the lockout tube 314 to intersectwith centerline 454 of shaft 406, resulting in the elimination of torquein the lockout tube 314, as described in more detail below. In someinstances, the centerlines 318 and 454 may be slightly offset due toslight variations in size of the components, movement of the differentcomponents, or variations in components, for example. These slightvariations may produce an offset between the centerlines 318 and 454that, in some cases, may be unavoidable. However, for the purposes ofthe present disclosure, intersection of the centerlines 318 and 454 isintended to encompass the slight offsets therebetween which may occur.

As shown in FIG. 5 , rotation of the lockout tube 314 in the directionof arrow 456 to a first position results in the float arms 308 beingplaced into a fully retracted position, which corresponds to the rigidconfiguration of the float arms 308 and cutterbar, such as cutterbar216. Rotation of the lockout tube 314 in the direction of arrow 458 to asecond position results in the float arms 308 being placed in a fullyextended position, which corresponds to the flexible configuration ofthe float arms 308 and cutterbar.

FIGS. 4, 6, and 7 illustrate actuation of the lockout system 326 betweenthe flexible configuration and the rigid configuration. In FIG. 6 , thelockout system 326 is in the flexible configuration in which thefloating arms 308 are in a fully extended. As a result, the float arms308 are freely pivotably about pin 451, and each of the float arms 308coupled to the lockout system 326 are able to pivot independently of theother float arms 308. Although the present example describes a lockoutsystem that can be included on a single wing of a header, in otherimplementations, a single lockout system operable to position all of thefloat arms of a header between the flexible configuration and a rigidconfiguration may be used.

Referring to FIGS. 4 and 6 , the lockout tube 314 is angularly orientedin the second position such that the biasing component 412 is unloaded,other than a preload that may be applied to the biasing component 412.With the lockout tube 314 in the second position, the float arms 308 arefreely pivotable about the pin 451, allowing the float arms 308 tofollow a contour of the ground when the float arms 308 are placed incontact with the ground. As the lockout tube 314 is rotated in thedirection of arrow 456, the shaft 406 translates relative to and rotateswith the pin 420. As a result, the shaft 406 is both rotated andtranslated towards the lockout tube 314. As shown in FIG. 6 , the shaft406 is displaced to cause the flange 426 to come into contact with thepin 420. Further rotation of the lockout tube 314 in the direction ofarrow 456 results in further displacement and rotation of the shaft 406,which, in turn, causes further compression of the biasing component 412.

With the flange 426 in contact with the pin 420, as the lockout tube 314continues to be rotated in the direction of arrow 456, the float arm 308is pivoted about the pin 451 in the direction of arrow 461. Moreover, asthe shaft 406 is pivoted in the direction of arrow 460, an amount oftorque applied to the lockout tube 314 decreases as the centerline 454of the shaft 406 approaches the centerline 318 of the lockout tube 314.

FIG. 7 shows the lockout system 326 in the rigid configuration. As shownin FIG. 7 , the lockout tube 314 is moved into the first position. Asthe lockout tube 314 is moved from the position show in FIG. 6 to theposition shown in FIG. 7 , the float arms 308 are retracted as a resultof the contact between the flange 426 and the pin 420. With the lockingsystem 326 in the rigid configuration, the float arms 308 are fullyretracted and in abutting contact with the cross tube, such ascross-tube 212, or another component of the frame 300; the lockout tube314 resides in the curved recess 437 formed by the second link 438; andthe centerline 454 of the shaft 406 intersects the centerline 318 of thelockout tube 314. As a result of the intersection of the centerline 454and the centerline 318, toque applied to the lockout tube 314 is reducedto approximately zero. Further, with the float arms 308 in the rigidconfiguration, the cutterbar is also placed into a straight and rigidconfiguration.

With the torque applied to the lockout tube 314 being effectively zerowhen the float arms 308 are in the retracted and rigid configuration, asize of lockout tube 314 may be reduced, which results in a weight,size, and cost reduction. Additionally, compression of the biasingcomponent 412 provides a force that is sufficient to retract all of thefloat arms 308 into abutting contact with a component of the frame 300,such as a cross-tube similar to cross-stube 212, notwithstanding anydimensional variations imparted to the frame 300 during manufacturing,for example. Consequently, the lockout system 326 is operable to actuateall the float arms 308 into contact with a portion of the frame 300without preliminary adjustment during manufacturing or subsequentadjustment when the header has entered use. Thus, the lockout system 326avoids an adjustment preformed during manufacturing or sometimethereafter, such as by a technician or user, to ensure full actuation ofthe float arms 308 into the rigid configuration.

Automatic actuation of a lockout system, which may be similar to lockoutsystem 326, in response to extension and retraction of a gauge wheel isdescribed with reference to FIGS. 8 and 9 . FIG. 8 is a side view of aportion of the example header 300 with the gauge wheel 310 in aretracted position, and FIG. 9 is a side view of the portion of theheader 300 with the gauge wheel 310 in an extended position. The gaugewheel 310 and arm 312 define a gauge wheel assembly 800. The gauge wheelassembly 800 is pivotably coupled to the mounting bracket 306 at a pivot802 and is rotatable about a pivot axis 804. The pivot 802 is defined bya shaft, bolt, or other component on which the gauge wheel assembly 800rotates.

The linkage 320 connects the gauge wheel assembly 800 and the lockouttube 314 and, hence, the lockout system 326. The second link 324includes a pin 806 that is received into and a slot 808 defined by thethird link 325. The pin 806 is slidable within the slot 808. In otherimplementations, the pin 806 and slot 808 are omitted, and the secondlink 324 and third link 325 are pivotably connected.

When the gauge wheel assembly 800 is deployed from the stowed orretracted position, such as by an input made by an operator of a header300 or agricultural vehicle to which the header 300 is coupled, thegauge wheel assembly 800 rotates in a direction of arrow 801 about thepivot axis 804. In some instances, an actuator is used to position thegauge wheel assembly 800 between the retracted position and the extendedposition. In some implementations, the actuator is a hydraulic cylinder,a pneumatic cylinder, an electrically operated linear actuator, a rotaryactuator, or some other actuator that is operable to move one or moregauge wheel assemblies between a retracted position and an extendedposition. In response, the second link 324 pivots relative to the firstlink 322 at pivot 810 while the pin 806 of the second link 824 slideswithin the slot 808. As a result of the relative, sliding movement ofthe second link 324 and the third link 325 coupled to the lockout tube314, the lockout system 326 remains in an unaltered condition. In someinstances, the third bracket 325 is fixedly attached to the lockout tube314, such as with a fastener (e.g., a bolt) or welding, friction fit,keyed engagement, spline engagement, or by being integrally formed withthe lockout tube 314. Thus, in the illustrated implementation, thelockout system 326 remains in an unlocked condition, resulting in thefloat arms 308 being in an extended or flexible condition, during aportion of the deployment of the gauge wheel assembly 800. When the pin806 reaches a first end 812 of the slot 808, the send link 324 engagesthe third link 325, causing the third link 325 and lockout tube 314 torotate about centerline 318 in the direction of arrow 814.

In some implementations, the second link 324 and the third link 325engage each other (i.e., when the pin 806 of the second link 324 engagesthe first end 812 of the slot 808 of the third link 825) at selectedamount articulation of the gauge wheel assembly 800 between theretracted position and the extended position. For example, in someimplementations, the second link 324 and the third link 325 engage at anamount of articulation that results in the float arms 308 and thecutterbar of the header 302 being in the rigid configuration and 90percent of articulation of the gauge wheel assembly 800. In otherimplementations, the selected amount of articulation may be greater thanor less than 90 percent. In some implementations, the second link 324engages the third link 325 when the gauge wheel assembly 800 reaches aselected amount of articulation. For example, in some implementations,the second link 324 and the third link 325 engage each other when thegauge wheel assembly 800 reaches 90 percent of articulation from theretracted position to the extended position. Consequently, in suchexamples, over the remaining 10 percent of articulation, the lockoutsystem 326 moves the float arms 308 and cutterbar of the header 302 fromthe flexible configuration to the rigid configuration. Again, in otherimplementations, the selected amount of articulation at which the secondlink 324 engages the first link 325 may be greater than or less than 90percent.

As mentioned above, when the second link 324 and the third link 325engage, the third link 325 rotates in the direction of arrow 814,rotating the lockout tube 314 also in the direction of arrow 814. As thelockout tube 314 approaches full rotation (at which point the float arms308 are in the rigid configuration), a pin 816 included on a bracket 818coupled to the lockout tube 314 engages a retainer assembly 820. In someinstances, the bracket 818 forms part of the third link 325. Theretainer assembly 820 includes a retainer 822 that functions to captureand retain the bracket 818, locking the lockout tube 314 and maintainingthe associated float arms and cutterbar in the rigid configuration, asshown in FIG. 9 .

In the illustrated example of FIGS. 8 and 9 , the float arms andcutterbar are locked in the rigid configuration within the final tenpercent of extension travel of the gauge wheel assembly 800. That is, arange of motion of the gauge wheel assembly 100 is defined between theretracted position and the extended position. As the gauge wheelassembly 800 reaches a position at approximately 90 percent of travel ofthe range of motion from the retracted position to the extendedposition, the float arms and cutterbar begin to transition between theflexible configuration and the rigid configuration. By the time thegauge wheel assembly 800 reaches a position corresponding to 100 percentof ravel of the range of motion, the float arms and cutterbar are lockedinto the rigid configuration.

In other implementations, a location along the range of travel of thegauge wheel assembly 800 where the float arms and cutterbar begins totransition from the flexible configuration to the rigid configurationmay be any desired position. For example, in some instances, transitionof the float arms and cutterbar from the flexible configuration to therigid configuration is completed within the first 15 percent of therange of motion of the gauge wheel assembly 800. In other instances, thetransition from the flexible configuration to the rigid configurationmay begin at other points along the range of travel, such as 10 percent,20 percent, 25 percent, 30 percent, or 40 percent of the range oftravel. In still other implementations, the transition from the flexibleconfiguration to the rigid configuration may begin at other positions.Similarly, the point along the range of movement at which the float armsand cutterbar reach the rigid configuration may be any selected point.Further, a size of a portion of the range of movement over which thefloat arms and cutterbar transition from the flexible configuration tothe rigid configuration may be any desired amount. For example, thetransition may occur over five percent, 10 percent, or 15 percent of therange of motion of the gauge wheel assembly from the retraced positionto the extended position. In other implementation, a different amount ofthe range of motion may be used.

Still further, although numerous examples are provided in the context ofmoving the float arms and cutterbar into the rigid configuration fromthe flexible configuration, this description is also applicable tomovement of the float arms and cutterbar between the rigid configurationto the flexible configuration. For example, the float arms and cutterbarmay begin to transition at the 90 percent point of the range of motionof the gauge wheel assembly 800 from the extended position to theretracted position. In other implementations, the transition may occurat other points along the range of motion, such as at 10 percent, 20percent, 25 percent, 30 percent, or 40 percent of the range of travel.However, in other instances, the transition may initiate at other pointsalong the range of motion. Further, in some implementations, the samepoint along the range of motion is used as the point where thetransition occurs from the flexible configuration to the rigidconfiguration and vice versa.

Referring to FIGS. 9 and 10 , as the float arms and cutterbar are placedinto the rigid configuration, the pin 816 provided on the bracket 818 isreceived into a recess 900 formed in the retainer 822 of the retainerassembly 820. A portion 902 of the retainer 822 forming a part of therecess 900 extends partially around the pin 816. That is, in someimplementations, the recess 900 extends more than 180 degrees around aperimeter of the pin 816 so that the pin 816 remains retained within therecess 900, as described in more detail below.

The retainer assembly 820 includes the retainer 822 that defines therecess 900, a bracket 902 pivotably coupled to the retainer 822 at apivot 904, a rod 906 extending from the bracket 902, and a spring 908retained on the rod 906. The rod 906 is coupled to a bracket 910, andthe spring 908 is captured between the brackets 902 and 910. In someimplementations, the spring 908 is preloaded (e.g., stretched) betweenthe brackets 902 and 910, causing the spring 908 to impart a pullingforce on the bracket 902 that pulls the bracket 902 in the direction ofarrow 912. The retainer 822 is pivotably coupled to the mounting bracket306 at a pivot 914.

The rod 906 includes an elongated portion 907 and an enlarged portion909. The elongated portion 907 extends through an opening 916 formed ina flange 917 of the bracket 902. The enlarged portion 909 abuts theflange 917 of the bracket 902. The rod 906 is retained on the bracket902 by engagement between the enlarged portion 909 of the rod 906 andthe flange 917 of the bracket 902, and the rod 906 is retained on thebracket 910, such as by a fastener 918. For example, in some instances,an end of the rod 906 is threaded and threadingly mates with a fastener920, such as a nut. Consequently, the rod 906 is captured betweenbrackets 902 and 910. In some implementations, the rod 906 and thebracket 902 form an integral component.

The spring 908 is secured to the bracket 902 and the bracket 910 suchthat the spring 908 is stretched between the bracket 902 and bracket910. For example, in some implementations, the spring 908 engages theenlarged portion 909 of the rod 906, such as an end surface 919 ofenlarged portion. Further, the elongated portion 907 of the rod 906extends through and is slidable within an opening 921 formed in thebracket 910.

As the pin 816 is received into the recess 900, the pin 816 engages toretainer 822, causing the retainer 822 to pivot about the pivot 914 afew degrees in the direction of arrow 924. Because the pivots 904 and914 are offset from each other by an amount D relative to a line 922that is parallel to a direction of force applied by the spring 908(which, in this example, passes through a centerline of the rod 906 anda center of the pivot 904), causes further expansion of the spring 908(i.e., further stretching of the spring 908). As a result, a forcegenerated by the spring 908 increases, generating a moment that biasesthe retainer 822 to move in a direction of arrow 926 about the pivot914. When the pin 816 is fully received into the recess, the retainer822 rotates back in the direction of arrow 926 in response to thegenerated moment and captures the pin 816 in the recess 900. The shapeof the recess 900 in combination with the moment created by the biasingforce produced by the spring 908 captures and prevents the pin 816 frombeing removed from the recess 900. Consequently, the retainer assembly820 captures the pin 816 and the moment generated by the spring 908(i.e., the biasing of the retainer 822 in the direction of arrow 926about the pivot 914) maintains the float arms and cutterbar in the rigidconfiguration.

In other implementations, the spring 908 is placed in a compressedstate, as opposed to a stretched state. For example, relocating thepivot 914 to a location between the recess 900 and the line 922 causesthe spring 908 to be compressed in response to rotation of the retainer822 in the direction of arrow 924. In such instances, the spring 908 maybe preloaded by placing the spring 908 in compression. Thus, the spring908 may be placed in tension (i.e., stretched) or compression to providethe locking functionality of the retainer assembly 820, such as byaltering a position of the pivot 914 relative to the recess 900 and theline 922.

With continued reference to FIGS. 9 and 10 , as the gauge wheel assembly800 is retraced (i.e., by the rotation of the gauge wheel assembly 800in the direction of arrow 803 about pivot axis 804 from the extendedposition to the retracted position), the pin 806 slides within the slot808 as the second link 324 moves relative to the third link 325. As thegauge wheel assembly 800 continues to rotate in the direction of arrow803, the pin 806 reaches and engages the second end 807 of the slot 808,causing engagement of the second link 324 and the third link 325. Inresponse, the third link 325 and bracket 818 rotate in the direction ofarrow 805 about centerline 318. In turn, the pin 816 overcomes retentionby the retainer 822 and is removed from the recess 900, and the floatarms and cutterbar are released from the rigid configuration. Removal ofthe pin 816 from the recess 900 cause a slight rotation of the retainer822 about pivot 914 in the direction of arrow 924. The biasing forcegenerated by the spring 908 in response causes the retainer 822 torotate in the direction of arrow 926 upon release of the pin 816. As aresult, the float arms and cutterbar are moved from the rigidconfiguration to the flexible configuration.

FIGS. 11-14 illustrate another example actuation system 1100 foractuating a lockout system that may be similar to the lockout system326, described earlier. The actuation system 1100 includes a lever 1102coupled to a gauge wheel assembly 1104 (which may be similar to thegauge wheel assembly 229 or gauge wheel assembly 800), a rocker arm 1106coupled to a lockout tube 1108 (which may be similar to lockout tube314), and a retainer 1110 that is pivotably coupled to a mountingbracket 1112 (which may be similar to the mounting bracket 306). Thelockout tube 1108 is coupled to the lockout system in manner that may besimilar to the manner described above with respect to lockout tube 314and lockout system 326. Rotation of the lockout tube 1108 operates toactuate the lockout system to move one or more float arms (which may besimilar to float arms 308) and a cutterbar (which may be similar tocutterbar 132) between a rigid configuration and a flexibleconfiguration, as described earlier.

In the illustrated example, the rocker arm 1106 includes a semicircularportion 1114 that abuts the lockout tube 1108, and the rocker arm 1106is secured to the lockout tube 1108 using fasteners 1116 that extendthrough the lockout tube 1108 and the semicircular portion 1114. Inother implementations, the rocker arm 1106 and the lockout tube 1108 canbe joined in other ways, such as by welding or by using an adhesive orby integrally forming the rocker arm 1106 with the lockout tube 1108. Asshown, the rocker arm 1106 includes first and second sides 1118 and1120, laterally offset from each other, with first and second pins 1122and 1124 extending therebetween. The first and second pins 1122 and 1124engage respective recesses 1126 and 1128 formed in the lever 1102 andretainer 1110, as described in more detail below.

The retainer 1110 is pivotable on the mounting bracket 1112 about apivot 1130. In the illustrated example, the retainer 1110 is pivotablymounted the mounting bracket 1112 via bracket 1132. During actuation ofthe actuation system 1100, the lever 1102 and the retainer 1110 arereceivable between the first and second sides 1118 and 1120 of therocker arm 1106.

The retainer 1110 forms part of a retainer assembly 1134. The retainerassembly 1134 includes the retainer 1110, a bracket 1136 pivotablycoupled to the retainer 1110 at a pivot 1138, a rod 1140 capturedbetween the bracket 1136 and a bracket 1142 attached to the mountingbracket 1112, and a spring 1144 retained on the rod 1140 between thebracket 1136 and the bracket 1142. The rod 1140 includes an elongatedportion 1146 and an enlarged portion 1148. The elongated portion 1146extends through an opening 1150 formed in a flange 1152 of the bracket1136 and through an opening 1154 formed in the bracket 1142. The rod1140 is retained on the bracket 1142 by a fastener 1156. For example, insome instances, an end of the rod 1140 is threaded and threadingly mateswith the fastener 1156, which may be a nut. Consequently, the rod 1140is captured between brackets 1136 and 1142. A position of the fastener1156 along the elongated portion 1146 of the rod 1140 defines how farthe bracket 1136 is able to move away from the bracket 1142 and, thus,how far the spring 1144 is able to expand. In some implementations, therod 1140 and the bracket 1136 are integrally formed.

In some implementations, the spring 1144 is preloaded (e.g., compressed)between the brackets 1136 and 1142, causing the spring 1144 to impart apushing force on the bracket 1136 that pushes the bracket 1136 in thedirection of arrow 1158 (parallel to centerline 1160 of the rod 1140),tending to rotate retainer 1110 in the direction of arrow 1162 aboutpivot 1130. The retainer 1110 is pivotably coupled to the mountingbracket 1112 at a pivot 1130.

Operation of the actuation system 1100 is described with reference toFIGS. 13 and 14 . In operation, with the gauge wheel assembly 1104 inthe retracted position, extension of the gauge wheel assembly 1104 isselected, such as by an operator of an agricultural implement thatincludes the gauge wheel assembly 1104. In response, the gauge wheelassembly 1104 is rotated about a pivot axis 1162 of pivot 1164 in thedirection of arrow 1166. As the lever 1102 is rotated with the gaugewheel assembly 1104, the interaction between the recess 1126 and thefirst pin 1122 causes the rocker arm 1106 to rotate in the direction ofarrow 1168 about a centerline 1170 of the lockout tube 1108. Beingcoupled with the rocker arm 1106, the lockout tube 1108 similarlyrotates about the centerline 1170 in the direction of arrow 1168, movingthe float arms and cutterbar from the flexible configuration to therigid configuration.

As the gauge wheel assembly 1104 continues to move into the extendedposition, the lever 1102 continues to rotate the rocker arm 1106 in thedirection of arrow 1168, causing the second pin 1124 to engage theretainer 1110 and be received within the second recess 1128. In someinstances, prior to the second pin 1124 being inserted into the secondrecess 1128, the second pin 1124 contacts an outer edge of the retainer1110, causing the retainer 1110 to rotate a few degrees in the directionof arrow 1172. Thereafter, the second pin 1124 enters the second recess1124, and the retainer 1110 rotates a few degrees back in the directionof arrow 1162 in response to a spring force generated by the spring1144.

With the second pin 1124 received within the second recess 1128, thesecond pin 1124 causes the retainer 1110 to rotate in the direction ofarrow 1172 about pivot 1130. With the second pin full received into thesecond recess 1128 and the retainer 1110 fully rotated in response,continued rotation of the gauge wheel assembly 1104 cause the first pin1122 to be withdrawn from the recess 1126. As a result, rotation of therocker arm 1106 ceases. At this point, the lockout tube 1108 is fullyactuated to cause the float arms and cutterbar to be locked into therigid configuration.

Further, as a result of rotation of the retainer 1110 in the directionof arrow 1172, the retainer 1110 displaces the bracket 1136 in thedirection of arrow 1174, parallel to the centerline 1160 of the rod1140, compressing the spring 1144. Compression of the spring 1144 (alongwith any preload applied to the spring 1144) produces a biasing force inthe direction of arrow 1158. A shape of the recess 1128 interacts withthe pin 1124 to prevent withdrawal of the pin 1124 from the recess 1128,and the produced biasing force generated by the spring 1144, incombination with the interaction between the pin 1124 and the recess1128, lock the rocker arm 1106 and the retainer assembly 1134 together.FIG. 14 shows a condition of the actuation system 1100 when the gaugewheel assembly 1104 is in the extended position.

To retract the gauge wheel assembly 1104, an input is provided, such asby the operator of the implement, to retract the gauge wheel assembly1104. In response, the gauge wheel assembly 1104 is rotated in thedirection of arrow 1176. As the gauge wheel assembly 1104 rotates in thedirection of arrow 1176, the lever 1102 engages the first pin 1122,causing the first pin 1122 to be received into the first recess 1126.Particularly, a finger 1135 extending along a side of the first recess1126 engages the first pin 1122 and directs the first pin 1122 into thefirst recess 1126 as the lever 1102 is rotated in the direction of arrow1176. With further rotation of the gauge wheel assembly 1104 in thedirection of arrow 1176, engagement between the first pin 1122 and thelever 1102 causes rocker arm 1106 and the lockout tube 1108 to rotate inthe direction of arrow 1178, which, in turn, causes the second pin 1124to be removed from the second recess 1128. At this point, the lockoutsystem unlocks, placing the cutterbar and float arms in the flexibleconfiguration. In some instances, removal of the second pin 1124 fromthe second recess 1128 cause the retainer 1110 to be rotated a fewdegrees in the direction of arrow 1172. This rotation of the retainer1110 causes an increased compression of the spring 1144. The biasingforce generated by the second spring 1144 produces a moment that rotatesthe second retain 1110 back to an initial position. FIG. 13 illustratesthe gauge wheel assembly 1104 in the fully retracted position.

In this way, the actuation system 1100 is operable to move the cutterbarand float arms into and between the rigid configuration and the flexibleconfiguration in response to movement of the gauge wheel assembly 1104.Although a single gauge wheel assembly 1104 is illustrated, an implementwithin the scope of the present disclosure may include more than onegauge wheel assemblies that operate in a similar manner.

Similar to the spring 908, the spring 1144 can be configured to operatein a stretched or compressed condition by, for example, altering aposition of the pivot 1130 relative to recess 1128 and longitudinal axis1160.

FIGS. 15 and 16 illustrate another example actuation system 1500 that isoperable to move a cutterbar, which may be similar to the cutterbar 132(shown in FIG. 1 ), and associated float arms, which may be similar tofloat arms 214 (shown in FIG. 2 ), between a locked, rigid configurationand an unlocked, flexible configuration in response to extension andretraction of a gauge wheel assembly 1502, which may be similar to gaugewheel assembly 1104. Although a single gauge wheel assembly 1502 isillustrated, in other implementations, additional gauge wheel assemblies1502 may be included.

Referring to FIG. 15 , the actuation system 1500 includes a cam 1504, arocker arm 1506, a retainer assembly 1508, and a spring 1510. In someimplementations, the cam 1504 is in the form of a plate that is coupledto an arm 1512 of the gauge wheel assembly 1502. The gauge wheelassembly 1502 includes the arm 1512 and a wheel pivotably coupled to thearm 1512. The wheel may be similar to the wheel 310, shown in FIG. 3 ,discussed earlier. The gauge wheel assembly 1502 is pivotably coupled toa mounting bracket 1516, which may be similar to mounting bracket 1112,described earlier. The rocker arm 1506 is fixedly attached to a lockouttube 1518, which may be similar to lockout tube 1108, described earlier.In some implementations, the rocker arm 1506 has a construction similarto that of the rocker arm 1106. That is, in some instances, the rockerarm 1506 includes first and second sides, which may be similar to thefirst and second sides 1118 and 1120 of rocker arm 1106, and pin 1519extends between the first and second sides. Thus, when the pin 1519 isreceived in recess 1544, as described below, the retainer 1520 isreceived between the sides of the rocker arm 1506.

The rocker arm 1506 rotates with the lockout tube 1518 relative to themounting bracket 1516. Further, the rocker arm 1506 may be attached tothe lockout tube 1518 in a variety of ways, such as those describedabove with respect to lockout tube 1108 and rocker arm 1106. The rockerarm 1506 includes the pin 1519 disposed on a first end 1523 of therocker arm 1506.

The retainer assembly 1508 has a construction that is similar to that ofthe retainer assembly 1134. The retainer assembly 1508 includes aretainer 1520 that is pivotable coupled to the mounting bracket 1516 viaa pivot 1521, a bracket 1522 pivotably coupled to the retainer 1520 at apivot 1524, a rod 1526 extending between the bracket 1522 and a bracket1528 attached to the mounting bracket 1516, and a spring 1530 capturedon the rod 1526 between the bracket 1522 and the bracket 1528. The rod1526 extends through and is movable in an opening 1532 formed in thebracket 1528, such as in the manner described above in the context ofrod 1140. Thus, the rod 1526 is movable in a direction parallel to alongitudinal axis 1534 of the rod 1526 relative to the bracket 1528, andan amount by which the spring 1520 is able to expand is limited by afastener 1525 or another component coupled to the rod 1526, therebylimiting an amount by which the rod is movable in the opening 1532.Thus, in some implementations, the rod 1526 is retained to the bracket1528 in a manner similar to that described above with respect to rod1140 and bracket 1142. In the illustrated example, the spring 1510 isconnected to a beam 1536 (which may be similar to beam 304) at a firstend 1538 via a bracket 1540 and, at a second end 1541, to a second end1542 of the rocker arm 1506. In other implementations, the spring 1510may be coupled to another part of the header, such as another part ofthe header frame, e.g., the mounting bracket 1516. The retainer 1520includes the recess 1544 that removably receives the pin 1519 of therocker arm 1506.

The cam 1504 includes a cam shape that engages with a counterpartprotrusion 1546 formed on the retainer 1520. As the cam 1504 rotateswith the gauge wheel assembly 1502, the cam shape of the cam 1504 andthe protrusion 1546 of the retainer 1520 operate to rotate the retainerabout pivot 1521.

FIG. 15 shows the gauge wheel assembly 1502 in the retracted position inwhich the float arms and cutterbar are in the flexible configuration,and FIG. 16 shows the gauge wheel assembly 1502 in the extended positionwith the actuation system 1500 configured such that the lockout tube1518 has locked the float arms and cutterbar in the rigid configuration.In normal operation, when the gauge wheel assembly 1502 is in theretracted position, the float arms of the agricultural implement are incontact with the ground. In the retracted position, the cam 1504 is incontact with the protrusion 1546 of the retainer 1520, maintaining theretainer 1520 in an unlocked configuration. In the unlockedconfiguration, the float arms and cutterbar, via the float arms, are inthe flexible configuration and are free to pivot about axis 1548. Asshown in FIG. 5 , this pivot axis is defined by one or more pins, suchas pin 451 in FIG. 5 .

Generally, the lockout tube 1518 is connected to a plurality of floatarms. When the cutterbar and float arms are in the flexibleconfiguration and the associated implement is moved through a field,such as during a harvesting operation, the float arms are allowed tofollow a contour of the ground, thus, causing the float arms to pivotabout axis 1548. If at least one of the float arms pivots downwards,i.e., in the direction of arrow 1549, the float arm causes the lockouttube 1518 and rocker arm 1506 to rotate in the direction of arrow 1551as a result of a lockout system similar to lockout system 326 couplingthe float arm to the lockout tube 1518. This position of the lockouttube 1518 and rocker arm 1506 is shown in FIG. 15 , and this position isthe prevailing one during an agricultural operation, such as harvesting.This is because, generally, at least one float arm is at least partiallyin a downwardly pivoted position, causing the lockout tube 1518 torotate in the direction of arrow 1551. In some implementations, thespring 1510 provides enough force to rotate the lockout tube 1518 andassociated rocker arms 1506 about axis 1552 in the direction of arrow1550 (such as to a position similar to that shown in FIG. 16 ) when allof the weight of the float arms is removed from the lockout tube 1518.Consequently, when moving the float arms and cutterbar from the flexibleconfiguration to the rigid configuration, all of the float arms arefully pivoted in the direction of arrow 1553, such as until each of thefloat arms contacts a stop, thereby removing all of the weight of thefloat arms and cutterbar from the lockout tube 1518. In response, aforced exerted by the spring 1510 to the lockout tube 1518 (via therocker arms 1506) causes the lockout tube 1518 and associated rockerarms 1506 to rotate in the direction of arrow 1550 and attain a positionsimilar to that shown in FIG. 16 . At this location, the float arms andcutterbar can be locked into the rigid configuration, as described inmore detail below.

With the weight of the float arms and cutterbar being supported by theground and as a result of the rotation to the lockout tube 1518 and therocker arm 1506 due to the spring 1510, the lockout tube 1518 ismaintained in a position similar to that of the lockout tube 314 shownin FIG. 7 . That is, the lockout tube 1518 is maintained in a positionthat is or is close to a locked position, as shown, for example, in FIG.7 (referred to as the first position in the description associated withFIG. 7 ). This rotation of the lockout tube 1518 and rocker arm 1506cause the pin 1519 to be received into the recess 1544 formed in theretainer 1520.

When the gauge wheel assembly 1502 is moved from the retracted positionto the extended position, such as by an actuator, the gauge wheelassembly 1502 rotates about pivot 1554 in a direction of arrow 1556. Asthe rotation of the gauge wheel assembly 1520 occurs, the cam 1504disengages from the protrusion 1546 of the retainer 1520, which, inreturn, causes the compressed spring 1530 to expand and exert a momenton the retainer 1520. The retainer 1520 rotates about pivot 1521 in thedirection of arrow 1531 in response to the moment, locking the rockerarm 1506 and the lockout tube 1518 into position. Further, locking ofthe lockout tube 1518 and the rocker arm 1506 into position by theretainer 1520 occurs before all of the weight of the float arms andcutterbar is removed from the ground. Consequently, the float arms andcutterbar are locked into position during an initial range of rotationduring extension of the gauge wheel assembly 1502. As rotation of thegauge wheel assembly 1502 continues to the point where all of the weightof the float arms and cutterbar is removed from the ground and is,therefore, no longer supported by the ground, the float arms andcutterbar are locked into the rigid configuration. FIG. 16 shows theactuation system 1500 in a configuration in which the float arms andcutterbar are locked in the rigid configuration.

Thus, the actuation system 1500 is operable to lock the float arms andcutterbar of an implement into a rigid configuration within a portion ofthe actuation of a gauge wheel assembly during movement from a retractedposition to an extended position. In some implementations, locking thefloat arms and cutterbar into the rigid configuration occurs within 15percent of the range of movement between the retracted position and theextended position. In other implementations, locking occurs at otherpercentages of movement. For example, locking may occur at five percent,ten percent, 20 percent, 25 percent, or 30 percent. In still otherimplementations, locking may occur at percentages of the movement of thegauge wheel assembly that is less than five percent, greater than 30percent, or at some point between the specific percentages described.

The gauge wheel assembly 1502 is retracted into the retracted positionto move the cutterbar and float arms from the rigid configuration intothe flexible configuration. Referring again to FIGS. 15 and 16 , withthe gauge wheel assembly 1502 in the extended position (shown in FIG. 16), the gauge wheel assembly 1502 is retracted, such as in response to anoperator input. During retraction, the gauge wheel assembly 1502 isrotated about the pivot 1554 in the direction of arrow 1558. Duringrotation of the gauge wheel assembly 1502, the cam 1504 engages theprotrusion 1546 of the retainer 1520, causing the retainer 1520 torotate in the direction of arrow 1560. This releases the pin 1519 fromthe recess 1544, thereby unlocking the lockout tube 1518 and rocker arm1506 and placing the float arms and cutterbar into the flexibleconfiguration. The gauge wheel assembly 1502 continues to rotate aboutthe pivot 1554 in the direction of arrow 1558 until the gauge wheelassembly 1502 reaches the retracted position, as shown in FIG. 15 .

Locking the cutterbar into the rigid configuration during a selectedamount of rotation of the gauge wheel assembly as the gauge wheelassembly is moved from the retracted position to the extended positionis important because, in some instances, the gauge wheels may not befully deployed to the extended position. This may be due, for example,to user preference or ground topography. In any case, since the gaugewheels can be extended to any number of positions between the retractedposition and the extended position, it is desirous to have the cutterbarlocked into the rigid configuration for any of those gauge wheelassembly deployed positions. Therefore, the actuation system 1500 isoperable to place the float arms and cutterbar into a rigidconfiguration after a small amount of extension of the gauge wheelassembly 1502 and, in some case, almost immediate locking once the gaugewheel assembly 1502 has started to deploy away from the retractedposition. Consequently, the actuation system 1500 provides for providingthe float arms and cutterbar in the rigid configuration for a range ofdeployments of the gauge wheel assembly 1502 that is less than theextended position, which, in such cases may be referred to as a fullyextended position.

Without in any way limiting the scope, interpretation, or application ofthe claims appearing below, a technical effect of one or more of theexample implementations disclosed herein is to automatically move acutterbar of an agricultural implement between a rigid configuration anda flexible configuration in response to extension or retraction of agauge wheel (e.g., a gauge wheel assembly). Another technical effect ofone or more of the example implementations disclosed herein is toprovide for locking a cutterbar into a rigid configuration within aportion of a total amount of articulation of a gauge wheel duringdeployment of the gauge wheel into an extended position. This providesfor placing the cutterbar into a rigid configuration for differentamounts of deployment of the gauge wheel or gauge wheels.

While the above describes example implementations of the presentdisclosure, these descriptions should not be viewed in a limiting sense.Rather, other variations and modifications may be made without departingfrom the scope and spirit of the present disclosure as defined in theappended claims.

What is claimed is:
 1. A system for automatically configuring acutterbar of an agricultural implement comprising: a cutterbar; a floatarm engaged with the cutterbar; a gauge wheel assembly; and an actuationsystem that connects the float arm and the gauge wheel, the float armmovable, via the actuation system, in response to one of retraction andextension of the gauge wheel to move the cutterbar between a rigidconfiguration and a flexible configuration, the actuation systemcomprising: a rocker arm comprising a pin and pivotable about a firstaxis, the rocker arm coupled to the float arm; a retainer comprising: arecess that releasably receives the pin to selectively lock the pin intothe recess; and a protrusion; and a cam coupled to the gauge wheelassembly, the cam moveable with the gauge wheel assembly to selectivelyengage the protrusion of the retainer to move the retainer between alocked configuration and an unlocked configuration.
 2. The system ofclaim 1, wherein, when the gauge wheel assembly is in the retractedposition, the cam engages the protrusion of the retainer to release thepin from the recess, placing the retainer in the unlocked configurationand the cutterbar in the flexible configuration.
 3. The system of claim1, wherein extension of the gauge wheel assembly from the retractedposition to the extended position rotates the cam to release theretainer to cause the retainer to pivot and capture the pin into therecess, placing the retainer into the locked configuration and thecutterbar in the rigid configuration.
 4. The system of claim 3, whereina biasing force pivots the retainer in response to release by the cam.5. The system of claim 4, wherein the biasing force is generated by acompressed spring.
 6. The system of claim 1, wherein retraction of thegauge wheel assembly from the extended position to the retractedposition rotates the cam to engage the protrusion of the retainer,causing the retainer to release the pin from the recess, placing theretainer in an unlocked configuration and the cutterbar in the flexibleconfiguration.
 7. The system of claim 1, wherein the actuation systemfurther comprises a spring coupled to the rocker arm, wherein the springapplies a moment to the rocker arm to pivot the rocker arm in adirection that moves the pin towards the recess of the retainer.
 8. Thesystem of claim 7, wherein the moment applied to the rocker arm by thespring pivots the rocker arm towards the retainer when weight of thefloat arm is removed from the rocker arm.
 9. The system of claim 1,further comprising a retainer assembly, wherein the retainer assemblycomprises: the retainer; a shaft pivotably coupled to the retainer; anda spring disposed on the shaft and configured to apply a moment to theretainer.
 10. The system of claim 9, wherein the spring is compress inresponse to engagement of the protrusion of the retainer by the cam, andwherein the compressed spring pivots the retainer about a second axiswhen the cam disengages the protrusion of the retainer.
 11. A method formoving a cutterbar of an agricultural implement between a rigidconfiguration and a flexible configuration in response to articulationof a gauge wheel of the agricultural implement between a retractedconfiguration and an extended configuration, the method comprising: oneof extending and retracting a gauge wheel of an agricultural implement;and simultaneously one of moving the cutterbar into a flexibleconfiguration in response to retraction of the gauge wheel and movingthe cutterbar into a rigid configuration by an actuation system that isoperated in response to retraction of the gauge wheel.
 12. The method ofclaim 11, wherein the actuation system comprises: a rocker armcomprising a pin and pivotable about the first axis, the rocker armcoupled to the float arm; a retainer comprising: a recess thatreleasably receives the pin to selectively lock the pin into the recess;and a protrusion; and a cam coupled to the gauge wheel, the cam moveablewith the gauge wheel assembly to selectively engage the protrusion ofthe retainer to move the retainer between a locked configuration and anunlocked configuration.
 13. The method of claim 12, whereinsimultaneously one of moving the cutterbar into a flexible configurationin response to retraction of the gauge wheel and moving the cutterbarinto a rigid configuration by an actuation system that is operated inresponse to retraction of the gauge wheel comprises: extending the gaugewheel from the retracted position to the extended position; pivoting thecam in response to extension of the gauge wheel to disengage the camfrom the protrusion of the retainer; and receiving the pin into therecess in response to disengagement of the cam from the protrusion ofthe retainer, thereby locking the cutterbar into the rigidconfiguration.
 14. The method of claim 13, further comprising pivotingthe rocker arm in a direction that moves the pin towards the recess ofthe retainer.
 15. The method of claim 14, wherein pivoting the rockerarm comprises applying a moment to the rocker arm with a spring.
 16. Themethod of claim 14, wherein pivoting the rocker arm in a direction thatmoves the pin towards the recess of the retainer comprises removingweight of the float arm from the rocker arm so that a moment applied tothe rocker arm is great enough to pivot the rocker arm in the directionthat moves the pin towards the recess of the retainer.
 17. The method ofclaim 12, wherein simultaneously one of moving the cutterbar into aflexible configuration in response to retraction of the gauge wheel andmoving the cutterbar into a rigid configuration by an actuation systemthat is operated in response to retraction of the gauge wheel comprises:retracting the gauge wheel from the extended position to the retractedposition; pivoting the cam in response to retraction of the gauge wheelto engage the cam with the protrusion of the retainer; and releasing thepin from the recess in response to engagement of the cam with theprotrusion of the retainer, thereby unlocking the cutterbar and placingthe cutterbar into the flexible configuration.
 18. An agriculturalimplement that automatically configures a cutterbar between a rigidconfiguration and a flexible configuration, the agricultural implementcomprising: a frame; a gauge wheel assembly coupled to the frame andmoveable between an extended position and a retracted position; a floatarm pivotably coupled to the frame; a cutterbar engaged with the floatarm, the cutterbar moveable between a rigid configuration and a flexibleconfiguration in response to rotation of the float arm; and an actuationsystem that connects the float arm and the gauge wheel assembly, thefloat arm movable, via the actuation system, in response to one ofretraction and extension of the gauge wheel to move the cutterbarbetween the rigid configuration and the flexible configuration, theactuation system comprising: a rocker arm comprising a pin and pivotableabout a first axis, the rocker arm coupled to the float arm; a retainercomprising: a recess that releasably receives the pin to selectivelylock the pin into the recess; and a protrusion; and a cam coupled to thegauge wheel assembly, the cam moveable in response to movement of thegauge wheel assembly to selectively engage the protrusion of theretainer to move the retainer between a locked configuration and anunlocked configuration.
 19. The agricultural implement of claim 18,wherein extension of the gauge wheel assembly from the retractedposition to the extended position rotates the cam to release theretainer to cause the retainer to pivot and capture the pin into therecess, placing the retainer into the locked configuration and thecutterbar in the rigid configuration.
 20. The agricultural implement ofclaim 18, wherein retraction of the gauge wheel assembly from theextended position to the retracted position rotates the cam to engagethe protrusion of the retainer, causing the retainer to release the pinfrom the recess, placing the retainer in an unlocked configuration andthe cutterbar in the flexible configuration.